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28 Model which is defined as ηts = h01 − h03 = ∆W (3-11) where h0x is the stagnation enthalpy at station x, h3ss is the point of complete isentropic expansion shown in Figure 3-11, ∆W is the specific work of the turbine, c3 is the absolute velocity of fluid flow. h01 −h3ss ∆W + 1c2 +(h3 −h3s)+(h3s −h3ss) 23 Figure 3-11: h-s diagram of the radial turbine expansion The passage enthalpy losses can be expressed as a fraction of the exit kinetic energy relative to the nozzle row and the rotor, i.e., h 3 − h 3 s = 1 w 32 ζ R 2 h3s − h3ss = 1c2ζN (T3/T2) 2 (3-12) h :< where ζR and ζN are loss coefficients at the rotor and nozzle respectively, w3 is the relative velocity of fluid flow, c2 is the absolute velocity of fluid flow, Tx is the static temperature at station x. Using (3-12) in (3-11) we get, 1222 −1 ηts = 1 + 2(c3 + w3ζR + c2ζN T3/T2)/∆W (3-13) The nozzle and rotor loss coefficients are assumed to be 0.1 and 1.0 respectively based on the range of practical values for well-designed nozzles and rotors given by Dixon [17]. Equation (3-13) is valid for nominal design point calculations(incidence-free operation). The validity can be extended to off-design operation by including an incidence loss coefficient while evaluating the velocity coefficient in the rotor [46]. Benson [47] presents a review of the method to Akshay Hattiangadi Master of Science Thesis W W W W : W W W WPDF Image | Working Fluid Design for Organic Rankine Cycle
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